JP3183237B2 - Vibration device for variable vibration table - Google Patents
Vibration device for variable vibration tableInfo
- Publication number
- JP3183237B2 JP3183237B2 JP32078697A JP32078697A JP3183237B2 JP 3183237 B2 JP3183237 B2 JP 3183237B2 JP 32078697 A JP32078697 A JP 32078697A JP 32078697 A JP32078697 A JP 32078697A JP 3183237 B2 JP3183237 B2 JP 3183237B2
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- shaft
- shafts
- vibration table
- eccentric
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Description
【0001】[0001]
【発明の属する技術分野】この発明はブロック成形機等
に用いる上下振動のみを発生する振動テーブルに適する
可変振幅型振動テーブル用振動装置に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibrating device for a variable amplitude type vibration table suitable for a vibration table which generates only vertical vibration used in a block molding machine or the like.
【0002】[0002]
【従来の技術】一般に、偏心重錘を備えた振動軸をもっ
て振動テーブルに振動を与える振置は旧くから各種知ら
れている。例えば、コンクリートブロック成形機におけ
る振動テーブルとしては、特開平2−80203号公報
に示される様にブロック原料を充填する型枠を受ける振
動テーブル本体の下面位置に、夫々油圧にて重錘部位置
を直接変えられる二重軸構成の振動軸体を2基配置し、
各油圧ピストンの摺動をもって重錘部の位置を移動し振
幅を変えるようにしたものなどがある。2. Description of the Related Art In general, there have been known various types of vibrating apparatuses that vibrate a vibration table with a vibration shaft having an eccentric weight. For example, as a vibration table in a concrete block molding machine, as shown in Japanese Patent Application Laid-Open No. 2-80203, the position of the weight portion is hydraulically positioned at the lower surface position of the vibration table body that receives the formwork filled with the block material. Two vibration shafts with a double shaft configuration that can be directly changed are arranged,
There is one in which the position of the weight is moved by sliding each hydraulic piston to change the amplitude.
【0003】[0003]
【発明が解決しようとする課題】しかし、1本の軸を内
筒と外筒とする二重軸構成の振動機構では、振動のアン
バランスの位置を位相のずれをもって行うには構成が複
雑過ぎて重錘部の位置制御が難しく、且つ装置への組み
込みが容易でなく、またメンテナンス等も面倒なものと
なっていた。However, in a vibration mechanism having a dual-shaft configuration in which one shaft is an inner cylinder and an outer cylinder, the structure is too complicated to perform the vibration unbalance position with a phase shift. Therefore, it is difficult to control the position of the weight portion, it is not easy to incorporate the weight into the device, and the maintenance is troublesome.
【0004】また、先に本願出願人が提示した二重軸構
成の振動軸を2本、振動テーブルの中央部に組み込み
し、この内筒軸を重錘構成とする不平衡軸とし、該不平
衡軸に捩じれカム溝を設け、この捩じれカム溝に嵌合す
る制御ピンを機械的に長手方向に移動させて重錘部の位
相を変え所定の振動を得る振動装置もあるが、このタイ
プとしても捩じれカム溝に対する制御ピンの摺動が円滑
でなく、且つずれ等も生じやすく振動テーブル全域に均
一な所定振動を得ることは困難であった。[0004] Further, two vibration shafts having a double shaft configuration previously proposed by the applicant of the present application are incorporated in the center of the vibration table, and this inner cylinder shaft is formed as an unbalanced shaft having a weight structure. There is a vibration device that provides a torsional cam groove on the balance shaft and mechanically moves a control pin fitted into the torsional cam groove in the longitudinal direction to change the phase of the weight portion to obtain a predetermined vibration. In addition, the sliding of the control pin with respect to the torsional cam groove is not smooth, and a shift or the like is apt to occur, and it is difficult to obtain a uniform predetermined vibration over the entire vibration table.
【0005】本発明は上記実情に鑑み、振動を誘起する
ための偏心重錘付き振動軸を2本一対としたものを2
組、振動テーブル内に左右対称に配置し、各組の振動軸
のうち夫々片方の振動軸の偏心重錘の位置を対称的に可
変するようにし、上記課題を解決する簡易タイプの可変
型振動テーブル用振動装置を提供することを目的とした
ものである。In view of the above-mentioned circumstances, the present invention relates to a construction in which two vibration shafts with eccentric weights for inducing vibration are paired.
A simple type of variable vibration that solves the above-mentioned problem by symmetrically disposing the eccentric weights of one of the vibration axes of each set in the vibration table of each set symmetrically in the vibration table. It is an object of the present invention to provide a table vibration device.
【0006】[0006]
【課題を解決するための手段】本発明は、所定の振動テ
ーブル内に夫々独立のモータで駆動し同期させる一対の
等価偏心重錘付き振動原軸を平行に軸承配設し、該各振
動原軸に夫々平行に前記等価偏心重錘と位相が変えられ
る互いに等価な偏心重錘付き振動従軸を軸承配設し4連
軸構成とすると共に、前記各振動従軸端に設けた歯付き
プーリに掛けるタイミングベルトを、夫々中央を枢着し
た揺動支持腕の上下端に配す歯付き張りプーリを介し前
記各振動原軸端の歯付きプーリに掛け渡し対称の逆転伝
達機構を形成し、且つ前記左右対向の揺動支持腕の枢軸
を、単一のシリンダで制御される連動リンク機構に連結
し対称回動とし、シリンダロッドの繰出し量に応じ振動
テーブルの上下振幅のみを最大から最小まで可変するよ
うにしたものである。According to the present invention, a pair of vibration source shafts with equivalent eccentric weights, which are driven by independent motors and synchronized with each other, are arranged in parallel in a predetermined vibration table. A vibration driven shaft with an eccentric weight equivalent to the equivalent eccentric weight, whose phase can be changed in parallel with the shafts, is arranged on the bearing to form a quadruple shaft configuration, and a toothed pulley provided at each end of the vibration driven shaft The timing belts to be hung are passed over the toothed pulleys at the ends of the respective vibrating shafts via toothed tension pulleys arranged at the upper and lower ends of a swing support arm having the center pivoted, respectively, to form a symmetrical reverse transmission mechanism, And, the pivots of the left and right opposing swing support arms are connected to an interlocking link mechanism controlled by a single cylinder for symmetrical rotation, and only the vertical amplitude of the vibration table from the maximum to the minimum according to the extension amount of the cylinder rod. It is made to be variable .
【0007】この場合、連動リンク機構が、シリンダの
ロッド端に連結したクランク部の中途に一方の揺動支持
腕の枢軸を配設し、クランク部先端に連結の連接棒端
を、他方の揺動支持腕の枢軸に配した連動杆端に連結し
てなる。In this case, the interlocking link mechanism arranges the pivot of one swing support arm in the middle of the crank connected to the rod end of the cylinder, and connects the connecting rod end connected to the tip of the crank to the other swing. It is connected to an interlocking rod end arranged on the pivot of the dynamic support arm.
【0008】また、請求項2に記載の発明は、請求項1
に記載のシリンダロッドが、振動テーブルの振動中に繰
出し自在となり連続的な可変を行うものである。[0008] The invention described in claim 2 is the first invention.
The cylinder rod described in (1) above can be extended freely during vibration of the vibration table and continuously varies.
【0009】この様に、振動装置は同期回転する等価偏
心重錘付き振動原軸を2本と、該振動原軸の偏心重錘と
位相が変えられる偏心重錘付き振動従軸を2本との計4
本の振動軸を用い、且つ各振動従軸を夫々振動原軸から
タイミングベルトを介し対称的に逆回転するようにし、
振動従軸側の偏心重錘の位相変更を、単一のシリンダに
連動リンク機構を介して無段階に連動するようにしたた
め、振動テーブルの振動可変は、全体としてテーブルの
左右位置に等価偏心重錘付き振動原軸と偏心重錘付き振
動従軸が2組対称となっていて、振動原軸と振動従軸の
双方の偏心重錘の位相の選定に起因し上下振動のみを最
大から最小まで発生する。As described above, the vibrating apparatus has two vibrating shafts with equivalent eccentric weights that rotate synchronously and two vibrating slave shafts with eccentric weights whose phase can be changed from that of the eccentric weights of the vibrating shaft. A total of 4
Using the vibration axes, and each of the vibration slave axes are symmetrically reversely rotated from the vibration original axis via a timing belt,
The phase change of the eccentric weight on the side of the vibration driven shaft is linked to a single cylinder in a stepless manner via an interlocking link mechanism. Two sets of oscillating shaft with weight and oscillating slave shaft with eccentric weight are symmetrical, and only vertical vibration from maximum to minimum due to selection of phase of eccentric weight of both oscillating shaft and slave shaft appear.
【0010】即ち、各振動従軸の偏心重錘の位置(位
相)が夫々の振動原軸の等価偏心重錘に対し上下対称位
置に設定されているときは、上下方向の振動は振動原軸
の等価偏心重錘と振動従軸の偏心重錘が上下方向にあっ
て対称位置となって相殺され、最小振幅となる。水平方
向(左右方向)の振動は、テーブルの中心に対しして2
組の振動原軸と振動従軸が対称配置となっているため相
殺され0となる。That is, when the position (phase) of the eccentric weight of each vibration driven shaft is set to be vertically symmetrical with respect to the equivalent eccentric weight of each vibration original shaft, the vibration in the vertical direction will be reduced. And the eccentric weight of the vibration slave shaft are vertically symmetrical and offset by symmetrical positions, and have a minimum amplitude. Horizontal (horizontal) vibration is 2 degrees with respect to the center of the table.
Since the set vibration source axis and the vibration slave axis are symmetrically arranged, they are offset to zero.
【0011】また、各振動従軸の偏心重錘の位置(位
相)が夫々の振動原軸の等価偏心重錘と同一方向の設定
では、上下方向の振幅は最大を得る。この振幅最小から
最大に至るすべての位相において、水平方向の振動は2
組の振動原軸の等価偏心重錘と振動従軸の偏心重錘が左
右対称且つ等価となるため、水平方向の振動は相殺され
0となる。When the position (phase) of the eccentric weight of each vibration driven shaft is set in the same direction as the equivalent eccentric weight of each vibration original shaft, the amplitude in the vertical direction is maximized. In all phases from the minimum to the maximum amplitude, the horizontal vibration is 2
Since the equivalent eccentric weight of the pair of vibration original shafts and the eccentric weight of the vibration slave shaft are bilaterally symmetric and equivalent, the vibration in the horizontal direction is canceled and becomes zero.
【0012】この振動テーブルは左右の振動従軸の等価
偏心重錘の位置の移動で上下方向の振幅が最大から最小
(停止)まで連続的に可変となる。但し、水平振動にあ
っては、あくまで2組の偏心重錘付き振動従軸と偏心重
錘付き振動原軸がテーブル中心に対し左右対称のため、
偏心重錘の位置が変わっても全体としては左右対称が維
持され、水平方向への振動は相殺されるので上下方向の
みの振幅が生ずる。In this vibration table, the amplitude in the vertical direction can be continuously varied from the maximum to the minimum (stop) by moving the position of the equivalent eccentric weight of the left and right vibration slave axes. However, in the case of horizontal vibration, the two sets of the vibration slave shaft with eccentric weight and the vibration original shaft with eccentric weight are symmetrical with respect to the table center.
Even if the position of the eccentric weight changes, the symmetry is maintained as a whole, and the vibration in the horizontal direction is canceled out, so that only the amplitude in the vertical direction occurs.
【0013】[0013]
【発明の実施の形態】以下、本発明の可変型振動テーブ
ル用振動装置を実施例の図に基づいて説明すれば、次の
通りである。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a vibration device for a variable vibration table according to the present invention.
【0014】図1乃至図6は偏心重錘(ウエイト)を回
転軸の長手方向片面に付けた振動軸を用いる実施例を示
す。1は所定の振動テーブル2の中心に対し左右位置に
夫々軸受3をもって平行に軸承配設した一対の等価偏心
重錘4付きの振動原軸で、この各振動原軸1は夫々独立
したモータ5よりベルト6を介し駆動されると共に、そ
の各軸端に設けた同期用歯車7を互いに噛合させて同期
回転させる構成としている。8は前記各振動原軸1の外
側位置に夫々平行配設する互いに等価な偏心重錘9付き
の振動従軸であり、この各偏心重錘9の偏心設定は、振
動従軸8自体の回動をもって前記振動原軸1の等価偏心
重錘4に対し適宜の位相が取れるようにしている。この
各振動従軸8の回転は各振動原軸1から適宜の伝達機構
を介し反転する構成である。この逆転伝達機構10の構
成は、振動従軸8の軸端に設けた歯付きプーリ11に掛
けた無端の両面型タイミングベルト12を、機体13側
の軸受14に軸承の支軸15に一体となる揺動支持腕1
6の上下部に取付けた歯付きプーリ17,17′に掛け
て反転させると共に、その両側を振動原軸1の軸端に取
付けた前記歯付きプーリ11と同一歯数の歯付きプーリ
18に掛け、振動従軸8と振動原軸1を反転の回転とす
る。FIGS. 1 to 6 show an embodiment using an oscillating shaft in which an eccentric weight (weight) is attached to one surface in the longitudinal direction of a rotating shaft. Reference numeral 1 denotes a vibration source shaft having a pair of equivalent eccentric weights 4 disposed in parallel with bearings 3 at right and left positions with respect to the center of a predetermined vibration table 2, and each vibration source shaft 1 is an independent motor 5. It is driven via a belt 6, and the synchronous gears 7 provided at the respective shaft ends are meshed with each other to rotate synchronously. Numeral 8 denotes a vibrating slave shaft having eccentric weights 9 which are disposed parallel to each other on the outer side of each of the vibration source shafts 1 and which are equivalent to each other. An appropriate phase can be obtained for the equivalent eccentric weight 4 of the vibration original shaft 1 by movement. The rotation of each of the vibration driven shafts 8 is reversed from each of the vibration original shafts 1 via an appropriate transmission mechanism. The structure of the reverse rotation transmission mechanism 10 is such that an endless double-sided timing belt 12 hung on a toothed pulley 11 provided at the shaft end of a vibration driven shaft 8 is integrally attached to a bearing 14 on a machine body 13 and a support shaft 15 of a bearing. Swing support arm 1
6 is mounted on the upper and lower parts of the vibration source shaft 1 and 17 'to be inverted, and both sides are mounted on a toothed pulley 18 having the same number of teeth as the toothed pulley 11 mounted on the shaft end of the vibration original shaft 1. The vibration slave shaft 8 and the vibration original shaft 1 are rotated in reverse.
【0015】19は前記左右一対となる縦使用の揺動支
持腕16,16を対称的に連動させる連動リンク機構
で、該連動リンク機構19は単一のシリンダ20のロッ
ド軸20aを、機体13側の軸受14′に軸承の一方の
支軸15を中央に配設したクランク部21の下端に連結
し、該クランク部21の上端に連結した連設棒22の先
端を前記他の軸受14に軸承の支軸15に設けた揺動杆
23の下端に連結したクランク構成であり、これら前記
全体構成で可変型振動テーブル用振動装置24となる。
図中、25は機体13と振動テーブル2間に装着した緩
衝部材である。Reference numeral 19 denotes an interlocking link mechanism for symmetrically interlocking the pair of left and right vertically used swing support arms 16, 16. The interlocking link mechanism 19 connects the rod shaft 20 a of the single cylinder 20 to the body 13. One of the shafts 15 of the bearing is connected to the lower end of a crank portion 21 disposed at the center of the bearing 14 ′ on the side, and the tip of a connecting rod 22 connected to the upper end of the crank portion 21 is connected to the other bearing 14. The crank structure is connected to the lower end of the swinging rod 23 provided on the support shaft 15 of the bearing, and the entire structure constitutes a vibrating device 24 for a variable vibration table.
In the figure, reference numeral 25 denotes a cushioning member mounted between the body 13 and the vibration table 2.
【0016】いまこの作用を説明すると、この可変型振
動テーブル用振動装置24は、例えば図7に示すような
コンクリートブロック成形機26に組み込みする。この
場合、振動装置24はブロック用型枠27を載置する振
動テーブル2に装着する。また、この振動テーブル2の
上方には型押し加圧部28を配置し,且つ型枠位置の左
右側に2種類の原料を給送するホッパー部29,29′
を配置している。Now, the operation will be described. The vibration device 24 for a variable vibration table is incorporated in a concrete block forming machine 26 as shown in FIG. 7, for example. In this case, the vibration device 24 is mounted on the vibration table 2 on which the block formwork 27 is placed. A stamping / pressing unit 28 is disposed above the vibration table 2, and hopper units 29 and 29 'for feeding two types of raw materials to the left and right sides of the mold position.
Has been arranged.
【0017】ここにおいて、コンクリートブロックの成
形としては、前記ホッパー部29,29′より給送する
ブロック原料a,a′を所定の型枠27内に順次充填
し、振動テーブル2に所定の振動を与えながら型押し加
圧部28を降下させてコンクリートブロックを形成する
ものである。Here, as the molding of the concrete block, block raw materials a and a 'fed from the hoppers 29 and 29' are sequentially filled in a predetermined formwork 27, and a predetermined vibration is applied to the vibration table 2. The embossing / pressing unit 28 is lowered while being applied to form a concrete block.
【0018】ここで、振動テーブル2に生ずる振動は、
振動テーブル2に軸承した4本の振動軸中、2本の振動
原軸1の等価偏心重錘4は同位置に配されるが、該各振
動原軸1に平行となる振動従軸8の偏心重錘9の設定位
置(位相)は、前記等価偏心重錘4に対し同一位置から
180°ずれる対称位置まで逆転伝達機構10と連動リ
ンク機構19の作動をもって可変するため、この等価偏
心重錘4と偏心重錘9の位相の選定により最大振幅から
最小振幅までの範囲の振動を得る。Here, the vibration generated in the vibration table 2 is:
The equivalent eccentric weights 4 of the two vibrating shafts 1 are arranged at the same position among the four vibrating shafts supported on the vibrating table 2. Since the set position (phase) of the eccentric weight 9 is variable by the operation of the reverse transmission mechanism 10 and the interlocking link mechanism 19 from the same position to the equivalent eccentric weight 4 to a symmetrical position shifted by 180 ° from the equivalent eccentric weight 4, the equivalent eccentric weight 9 is changed. By selecting the phase of the eccentric weight 4 and the eccentric weight 9, vibration in the range from the maximum amplitude to the minimum amplitude is obtained.
【0019】例えば、2本の振動原軸1の等価偏心重錘
4の偏心位置と平行となる2本の振動従軸8の偏心重錘
9の偏心位置が同一のときは(図3,図6のC参照)、
上下方向にあっては振動が増幅され最大振幅の上下振動
が生ずる。このとき、水平方向の振動は、振動テーブル
2にあって2組の等価偏心重錘4付き振動原軸1と偏心
重錘9付き振動従軸8がテーブル中心を堺とし左右位置
に対称となっているため、双方の振動が相殺され水平振
動0となる。For example, when the eccentric positions of the eccentric weights 9 of the two vibration driven shafts 8 which are parallel to the eccentric positions of the equivalent eccentric weights 4 of the two vibration original shafts 1 are the same (see FIGS. 3 and 3). 6 C),
In the vertical direction, the vibration is amplified and a vertical vibration of the maximum amplitude is generated. At this time, the vibration in the horizontal direction is such that two sets of the vibration original shaft 1 with the equivalent eccentric weight 4 and the vibration slave shaft 8 with the eccentric weight 9 are symmetrical with respect to the left and right positions with the table center as the center. As a result, both vibrations cancel each other out, resulting in zero horizontal vibration.
【0020】また、振動テーブル2の上下振動を、給
材,圧縮等の各工程又は成型高さ、原料(重量骨材,軽
量骨材)などに起因して変えたい場合、前記等価偏心重
錘付き振動原軸1と偏心重錘付き振動従軸8の状態か
ら、その偏心重錘4,9の位相を適宜角度分ずらせばよ
い。この偏心重錘9の回動操作としては、先ずシリンダ
20を適宜作動しそのロッド軸20aを繰り出せば、該
ロッド軸20a端のクランク部21が支軸15を支点と
して横回動するため、クランク部21の先端の連設棒2
2が連動し対称位置で対向する偏心重錘付き振動従軸8
側の揺動杆23を回動し、該揺動杆23と一体の支軸1
5を介し揺動支持腕16が連動される。If it is desired to change the vertical vibration of the vibration table 2 due to each step of material supply, compression, etc., or the molding height, raw materials (heavy aggregate, lightweight aggregate), etc., the equivalent eccentric weight is used. The phases of the eccentric weights 4 and 9 may be shifted by an appropriate angle from the state of the vibration original shaft 1 and the oscillating slave shaft 8 with eccentric weight. As the turning operation of the eccentric weight 9, first, the cylinder 20 is appropriately operated and its rod shaft 20a is extended, and the crank portion 21 at the end of the rod shaft 20a rotates sideways with the support shaft 15 as a fulcrum. Connecting rod 2 at the tip of the part 21
Oscillating slave shaft 8 with eccentric weights that are interlocked and oppose at symmetrical positions
The swinging rod 23 is rotated, and the support shaft 1 integrated with the swinging rod 23 is rotated.
The swinging support arm 16 is interlocked via 5.
【0021】ここで、シリンダロッド軸20aの繰出し
量が最大となれば、揺動支持腕16と対向の揺動支持腕
16が夫々支軸15,15の回動に起因して図2に示す
ようにハ字状に位置するものとなる。このとき、各揺動
支持腕16の上下端に設けた歯付きプーリ17,17′
中、上位の歯付きプーリ17が振動従軸8の歯付きプー
リ11側に寄る移動となり下位の歯付きプーリ17′は
歯付きプーリ11に対し離れる移動となり、これに掛け
たタイミングベルト12の移行につれ振動原軸1を固定
して考えた場合、同図2にあって右振動従軸8は反時計
廻りに、左振動従軸8は時計廻りに回転し、該振動従軸
8に付いた偏心重錘9が振動原軸1の等価偏心重錘4に
対し180°回転する対称のずれた位置に臨むものとな
る。Here, when the extension amount of the cylinder rod shaft 20a is maximized, the swing support arm 16 and the swing support arm 16 opposite to each other are shown in FIG. 2 due to the rotation of the support shafts 15 and 15, respectively. As shown in FIG. At this time, toothed pulleys 17 and 17 ′ provided at the upper and lower ends of each swing support arm 16.
The middle and upper toothed pulleys 17 move toward the toothed pulley 11 of the vibration driven shaft 8, and the lower toothed pulley 17 ′ moves away from the toothed pulley 11. 2, the right vibration slave shaft 8 rotates counterclockwise and the left vibration slave shaft 8 rotates clockwise in FIG. The eccentric weight 9 faces a symmetrically displaced position rotated by 180 ° with respect to the equivalent eccentric weight 4 of the vibration original shaft 1.
【0022】この様に、振動従軸8の偏心重錘9と振動
原軸1の偏心重錘4が上下の対称位置に臨めば、振動従
軸8と振動原軸1に発生する双方の振動は相殺される。
即ち、この状態下では上下方向の振幅は最小となる。勿
論、このときの水平方向の振動も全体として2組の振動
従軸8と振動原軸1が、振動テーブル2の中心位置より
左右対称に配置しているため、左右方向となる振動は相
殺される。即ち、水平方向の振動が0となる。As described above, if the eccentric weight 9 of the vibration driven shaft 8 and the eccentric weight 4 of the vibration original shaft 1 face vertically symmetrical positions, both vibrations generated in the vibration driven shaft 8 and the vibration original shaft 1 are generated. Are offset.
That is, under this condition, the amplitude in the vertical direction becomes minimum. Of course, the horizontal vibrations at this time are also totally symmetrical with respect to the center position of the vibration table 2 because the two sets of the vibration slave shaft 8 and the vibration original shaft 1 are arranged symmetrically with respect to the center position of the vibration table 2. You. That is, the horizontal vibration becomes zero.
【0023】また、シリンダ20のロッド軸20aの繰
出し量を、最大繰出しと最小繰出しの中途となる適宜の
中間位置で止めたとすれば、振動従軸8の偏心重錘9は
振動原軸1の等価偏心重錘4に対し任意のしかも左右同
一のずれた位相となり、上下振幅が最大と最小と中間の
任意振幅を得るようになる。このときも、基本的には水
平方向の振動は0である。即ち、この種の振動テーブル
2は上下方向のみの振動を生ずる。例えば、シリンダ2
0のロッド軸20aの繰出し量を中間位置で止めれば、
振動従軸8の偏心重錘9は振動原軸1の等価偏心重錘4
に対し90°ずれた位相となり、上下振幅が最大と最小
との中間振幅を得るようになる。If the amount of extension of the rod shaft 20a of the cylinder 20 is stopped at an appropriate intermediate position between the maximum extension and the minimum extension, the eccentric weight 9 of the vibrating slave shaft 8 will The phase is arbitrarily shifted left and right with respect to the equivalent eccentric weight 4, and the vertical amplitude becomes an arbitrary amplitude between the maximum, the minimum, and the middle. At this time, basically, the vibration in the horizontal direction is zero. That is, this type of vibration table 2 generates vibration only in the vertical direction. For example, cylinder 2
If the extension amount of the rod shaft 20a of 0 is stopped at the intermediate position,
The eccentric weight 9 of the vibration driven shaft 8 is the equivalent eccentric weight 4 of the vibration original shaft 1.
, The phase is shifted by 90 °, and an intermediate amplitude between the maximum and minimum amplitudes is obtained.
【0024】更に、この振動原理を図6に基づいて詳述
すれば、図6の(A)に示す如く2組の等価偏心重錘付
き振動原軸1A,1Bと偏心重錘付き振動従軸8A,8
Bが振動テーブルにあって左右位置で対称的に配置さ
れ、且つ振動原軸1A,1Bの等価偏心重錘4Aと4B
が下方で同一に位置し、両外側の振動従軸8A,8Bの
偏心重錘9A,9Bの位置が前記偏心重錘4A,4Bに
対し180°の位相ずれ(反対位置)となった場合、2
組の振動原軸1A(1B)の偏心重錘4A(4B)と振
動従軸8A(8B)の偏心重錘9A(9B)が反対位置
の対称のため、振動原軸1A,1Bと振動従軸8A,8
Bが振動すれば双方の振動は相殺され上下方向の振幅が
最小となる。このとき、水平方向の振動としては、2組
の振動原軸1A,1Bと振動従軸8A,8Bの偏心重錘
4A,4Bと9A,9Bが全体として左右対称且つ等価
の配置となるため、左右方向の振動は相殺され、水平方
向の振動も0となる。The principle of the vibration will be described in detail with reference to FIG. 6. As shown in FIG. 6A, two sets of vibration original shafts 1A and 1B with equivalent eccentric weights and a vibration slave shaft with eccentric weights are used. 8A, 8
B is symmetrically arranged at the left and right positions in the vibration table, and the equivalent eccentric weights 4A and 4B of the vibration original shafts 1A and 1B
Are located at the same position below, and the positions of the eccentric weights 9A and 9B of the vibrating slave shafts 8A and 8B on both outer sides are 180 ° out of phase (opposite positions) with respect to the eccentric weights 4A and 4B. 2
The set of eccentric weights 4A (4B) of the vibration source shafts 1A (1B) and the eccentric weights 9A (9B) of the vibration slave shafts 8A (8B) are symmetrical at opposite positions. Shaft 8A, 8
If B vibrates, both vibrations are canceled and the amplitude in the vertical direction becomes minimum. At this time, as the vibration in the horizontal direction, the eccentric weights 4A, 4B and 9A, 9B of the two sets of vibration original shafts 1A, 1B and the vibration driven shafts 8A, 8B have a symmetrical and equivalent arrangement as a whole. The vibration in the left-right direction is canceled, and the vibration in the horizontal direction becomes zero.
【0025】また、図6の(C)に示すように左右位置
にあって一対の振動原軸1Aと1Bの偏心重錘4Aと4
Bが下方で同一に位置し、その両外側の振動従軸8Aと
8Bの偏心重錘9Aと9Bも下方で同一の位置の状態で
は、振動原軸1A,1Bと振動従軸8A,8Bが回転す
ればその振動は増幅され上下方向に最大の振幅を得る。
このとき、左右方向の振動は、前記同様に全体としてテ
ーブル中心の左右対称の配置のために相殺され、水平方
向の振動も0となる。As shown in FIG. 6 (C), the eccentric weights 4A and 4A of the pair of vibration original shafts 1A and 1B are located at the left and right positions.
B is located at the same position on the lower side, and the eccentric weights 9A and 9B of the vibrating slave shafts 8A and 8B on both outer sides are also at the same position on the lower side, the vibration original shafts 1A and 1B and the vibrating slave shafts 8A and 8B When rotated, the vibration is amplified and the maximum amplitude is obtained in the vertical direction.
At this time, the vibration in the left-right direction is canceled out due to the symmetrical arrangement of the center of the table as a whole, as described above, and the vibration in the horizontal direction is also zero.
【0026】また、図6の(B)に示す如く偏心重錘9
A,9Bの位相を前記態様に対し中間位置をとる場合、
即ち、振動従軸8A,8Bの偏心重錘9A,9Bが振動
原軸1A,1Bの偏心重錘4Aと4Bの位置より90°
の位相ずれを取るときは、上下方向の振幅が、前記図6
の(C)の最大振幅と図6の(A)の最小振幅との中間
振幅を得る。このことは、振動従軸8A,8Bの偏心重
錘9A,9Bの設定位置の選択で、テーブルの上下振幅
を最大値から最小値までの所望値を得ることができる事
になる。As shown in FIG. 6B, the eccentric weight 9
When the phases of A and 9B are set at an intermediate position with respect to the above-described aspect,
That is, the eccentric weights 9A and 9B of the vibration driven shafts 8A and 8B are 90 ° from the positions of the eccentric weights 4A and 4B of the vibration original shafts 1A and 1B.
When the phase shift of FIG.
6 (A) and the minimum amplitude shown in FIG. 6 (A). This means that a desired value of the vertical amplitude of the table from the maximum value to the minimum value can be obtained by selecting the setting positions of the eccentric weights 9A and 9B of the oscillation slave shafts 8A and 8B.
【0027】[0027]
【発明の効果】上述の様に、本発明の可変型振動テーブ
ル用振動装置は同期する一対の偏心重錘付き振動原軸
と、この各両側に前記偏心重錘と位相が変えられる偏心
重錘付き振動従軸を配す4連軸構成とし、各振動従軸の
回転を振動原軸よりタイミングベルトをもって揺動支持
腕の上下端に配す張りプーリを介し逆転伝達とし、且つ
揺動支持腕を単一のシリンダで制御される連動リンク機
構に連結し揺動させ、揺動支持腕の上下の張りプーリ位
置の移動に応じるタイミングベルトのずれをもって振動
従軸自体を回動し、偏心重錘位置を移行し振動原軸の偏
心重錘とに位相ずれ招くようにしたため、この装置を振
動テーブルに組み込めば、該振動テーブルには上下振幅
のみを最大から最小まで無段階に可変でき、振動テーブ
ルの使用目的に応じた上下振動を与えることができる。
即ち、この振動テーブル用振動装置で良い点は、単一の
シリンダの作動だけで運転中に可変されるため、原料や
成型物の大きさ、工程などに対応し随時調整を可能とす
る。As described above, the vibrating device for a variable vibration table according to the present invention comprises a pair of synchronized vibrating shafts with eccentric weights, and eccentric weights whose phases can be changed on both sides thereof. A four-shaft configuration having a vibration driven shaft attached thereto, wherein the rotation of each vibration driven shaft is reversely transmitted through tension pulleys arranged at the upper and lower ends of a swing support arm with a timing belt from the vibration original shaft, and the swing support arm Is connected to an interlocking link mechanism controlled by a single cylinder and swings, and the oscillating slave shaft itself is rotated with a timing belt shift according to the movement of the tension pulley position above and below the swing support arm, and the eccentric weight Since the position is shifted to cause a phase shift with respect to the eccentric weight of the vibration original shaft, if this device is incorporated in a vibration table, only the vertical amplitude can be continuously changed from the maximum to the minimum in the vibration table. Depending on the purpose of use It can give the upper and lower vibration.
That is, the point that this vibrating device for a vibrating table can be changed during operation only by the operation of a single cylinder can be adjusted at any time according to the size and process of the raw material and the molded product.
【0028】しかも、このとき振動変化はタイミングベ
ルトを掛ける逆転伝達機構と連動リンク機構を、単一の
シリンダをもって連動させるだけのため取扱いが容易
で、且つ振動テーブルの振動運転中に振幅を変えられ
る。また、シリンダ自体を少なくとも振動テーブルの外
側に臨ませれば振動変化を目視的に監視することも可能
となり、シリンダロッド軸の繰出し量を見るだけで上下
方向のみの振動量が簡単にわかる。Further, at this time, since the vibration change at this time is easy only because the reverse rotation transmission mechanism and the interlocking link mechanism that hang the timing belt are linked by a single cylinder, the handling is easy, and the amplitude can be changed during the vibration operation of the vibration table. . Further, if the cylinder itself is at least outside the vibration table, it is possible to visually monitor the change in vibration, and the amount of vibration only in the vertical direction can be easily determined only by looking at the amount of extension of the cylinder rod shaft.
【0029】このことは、例えばコンクリートブロック
成形機の振動テーブル使用とした場合、その型枠への材
料供給,充填,圧縮等の各工程に対応し最適振幅に瞬時
に切換え、最短時間で所期の目的を達することができ、
生産性が向上すると共にブロック原料の違い等に応じて
振動を変える場合などに最適である。This means that, for example, when a vibration table of a concrete block molding machine is used, the amplitude is instantaneously switched to the optimum amplitude corresponding to each step of material supply, filling, compression and the like to the formwork, and the expected time is shortened in the shortest time. Can achieve the purpose of
It is most suitable for the case where the productivity is improved and the vibration is changed according to the difference of the block raw material and the like.
【0030】また、本発明は偏心重錘付き振動原軸を振
動テーブルに対し単に並列的に4本平行連設とするた
め、振動機構全体が簡略化されるので、各種の振動テー
ブルへの装着が可能となり、且つメンテナンスも容易と
なる等の効果を奏する。Further, in the present invention, since the four vibration source shafts with eccentric weights are simply connected in parallel to the vibration table in parallel, the whole vibration mechanism is simplified, so that it can be mounted on various vibration tables. And maintenance is also facilitated.
【図1】本発明の可変型振動テーブル用振動装置の一実
施例の要部を示す斜視図である。FIG. 1 is a perspective view showing a main part of an embodiment of a vibration device for a variable vibration table according to the present invention.
【図2】上下方向,水平方向の振幅を最小とした場合の
要部を示す同側面図である。FIG. 2 is a side view showing the main part when the amplitude in the vertical and horizontal directions is minimized.
【図3】上下方向の振幅を最大とし,水平方向の振動を
0とした場合の要部を示す同側面図である。FIG. 3 is a side view showing the main part when the amplitude in the vertical direction is maximized and the vibration in the horizontal direction is zero.
【図4】振動従軸の軸位を可変とする逆転伝達機構を示
す説明図である。FIG. 4 is an explanatory diagram showing a reverse rotation transmission mechanism that makes the axial position of a vibration slave shaft variable.
【図5】同逆転伝達機構を連動するための連動リンク機
構の説明図である。FIG. 5 is an explanatory diagram of an interlocking link mechanism for interlocking the reverse rotation transmission mechanism.
【図6】4連となる振動原軸と振動従軸における偏心重
錘の位置関係を示す図で、(A)は振動原軸の等価偏心
重錘と振動従軸の偏心重錘を上下対称位置に設定し、上
下方向の振幅を最小とする説明図であり、(B)は振動
原軸の等価偏心重錘に対し振動従軸の偏心重錘を90°
ずらした位相とし上下方向の振幅を中間の振幅とする説
明図であり、(C)は振動原軸の等価偏心重錘と振動従
軸の偏心重錘を夫々下方で同一位置に設定し、上下方向
の振動を最大とする説明図である。FIG. 6 is a diagram showing a positional relationship between an eccentric weight of a vibration source shaft and a vibration slave shaft in a quadruple series, and FIG. 6A is a vertical symmetric diagram of an equivalent eccentric weight of the vibration source shaft and an eccentric weight of a vibration slave shaft. FIG. 4B is an explanatory view in which the amplitude in the vertical direction is set to the minimum position, and FIG.
FIG. 4C is an explanatory diagram in which the vertical phase amplitude is set to the middle amplitude while the phase is shifted, and the equivalent eccentric weight of the vibration source shaft and the eccentric weight of the vibration slave shaft are set at the same position below, respectively. It is explanatory drawing which maximizes the vibration of a direction.
【図7】可変型振動テーブル用振動装置をコンクリート
ブロック成形機の振動テーブルに組み込む実施例を示す
説明図である。FIG. 7 is an explanatory view showing an embodiment in which a vibration device for a variable vibration table is incorporated into a vibration table of a concrete block molding machine.
1 振動原軸 2 振動テーブル 4 等価偏心重錘 5 モータ 8 振動従軸 9 偏心重錘 10 逆転伝達機構 11 歯付きプーリ 12 タイミングベルト 16 揺動支持腕 17、17′ 歯付きプーリ 18 歯付きプーリ 19 連動リンク機構 20 シリンダ 21 クランク部 22 連設棒 23 揺動杆 DESCRIPTION OF SYMBOLS 1 Vibration original shaft 2 Vibration table 4 Equivalent eccentric weight 5 Motor 8 Vibration slave shaft 9 Eccentric weight 10 Reverse rotation transmission mechanism 11 Toothed pulley 12 Timing belt 16 Oscillating support arm 17, 17 'Toothed pulley 18 Toothed pulley 19 Interlocking link mechanism 20 Cylinder 21 Crank part 22 Continuous rod 23 Swing rod
Claims (2)
タで駆動し同期させる一対の等価偏心重錘付き振動原軸
を平行に軸承配設し、該各振動原軸に夫々平行に前記等
価偏心重錘と位相が変えられる互いに等価な偏心重錘付
き振動従軸を軸承配設し4連軸構成とすると共に、前記
各振動従軸端に設けた歯付きプーリに掛けるタイミング
ベルトを、夫々中央を枢着した揺動支持腕の上下端に配
す歯付き張りプーリを介し前記各振動原軸端の歯付きプ
ーリに掛け渡し対称の逆転伝達機構を形成し、且つ前記
左右対向の揺動支持腕の枢軸を、単一のシリンダで制御
される連動リンク機構に連結してなり、かつ前記連動リ
ンク機構が、前記シリンダのロッド端に連結したクラン
ク部の中途に一方の揺動支持腕の枢軸を配設し、該クラ
ンク部先端に連結の連接棒端を、他方の揺動支持腕の枢
軸に配した連結杆端に、前記左右対向の揺動支持腕の枢
軸が対称回動するように連結することにより、前記シリ
ンダロッドの繰出し量に応じ振動テーブルの上下振幅の
みを最大から最小まで可変することを特徴とする可変型
振動テーブル用振動装置。1. A pair of equivalent eccentric weight-equipped vibration original shafts driven and synchronized by independent motors in parallel in a predetermined vibration table, and the equivalent eccentricity is provided in parallel with each of the vibration original shafts. The oscillating driven shafts with eccentric weights whose phases can be changed from the weighing weights are arranged on the bearings to form a quadruple-shaft configuration, and the timing belts to be hung on the toothed pulleys provided at the ends of the oscillating driven shafts are respectively centered. A symmetrical reverse transmission mechanism is formed to extend over the toothed pulleys at the ends of the respective vibration original shafts via toothed tension pulleys arranged at the upper and lower ends of a swinging support arm pivotally attached to the swinging support arm, and the left and right opposing swinging supports are formed. An arm pivot connected to an interlocking link mechanism controlled by a single cylinder , and
Link mechanism is connected to the rod end of the cylinder.
The pivot axis of one swing support arm is arranged in the middle of the
Connect the end of the connecting rod to the tip of the link
The pivoting arm of the left and right opposing swing support arms is
A vibrating device for a variable vibration table , wherein only a vertical amplitude of the vibration table is varied from a maximum to a minimum in accordance with an extension amount of the cylinder rod by connecting the shafts so as to rotate symmetrically. .
中に繰出し自在となり連続的な可変を行うことを特徴と
する請求項1に記載の可変型振動テーブル用振動装置。 2. The vibration table according to claim 1, wherein the cylinder rod is a vibration table.
It is characterized by being able to be fed out inside and making continuous adjustment
The vibration device for a variable vibration table according to claim 1.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32078697A JP3183237B2 (en) | 1997-11-21 | 1997-11-21 | Vibration device for variable vibration table |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32078697A JP3183237B2 (en) | 1997-11-21 | 1997-11-21 | Vibration device for variable vibration table |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH11156296A JPH11156296A (en) | 1999-06-15 |
JP3183237B2 true JP3183237B2 (en) | 2001-07-09 |
Family
ID=18125235
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JP32078697A Expired - Fee Related JP3183237B2 (en) | 1997-11-21 | 1997-11-21 | Vibration device for variable vibration table |
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JP (1) | JP3183237B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007080462A2 (en) * | 2006-01-10 | 2007-07-19 | Oto International (H.K.) Company Limited | Vibration device for massage device |
CN109974832A (en) * | 2019-04-03 | 2019-07-05 | 浙江华章科技有限公司 | A kind of algorithm of high-speed shaking system amplitude |
CN110948644A (en) * | 2019-12-30 | 2020-04-03 | 淄博松阳锆业科技有限公司 | Ceramic structure shaping vibrating device |
EP4134653A4 (en) * | 2020-04-08 | 2023-09-27 | Fukuoka University | Repeated moment generation device |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7442809B2 (en) | 2020-07-02 | 2024-03-05 | 学校法人福岡大学 | Repetitive moment generator |
CN111729834A (en) * | 2020-07-03 | 2020-10-02 | 北京实通科技有限公司 | Multi-shaft circular vibration exciter with synchronization function |
KR102520491B1 (en) * | 2020-12-29 | 2023-04-10 | 김인숙 | discharge rod vibrator of the electric melting furnace |
CN114274537B (en) * | 2021-12-31 | 2023-12-29 | 漳州砼艺建材有限公司 | Energy-saving and environment-friendly bionic stone processing equipment and processing method thereof |
-
1997
- 1997-11-21 JP JP32078697A patent/JP3183237B2/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007080462A2 (en) * | 2006-01-10 | 2007-07-19 | Oto International (H.K.) Company Limited | Vibration device for massage device |
WO2007080462A3 (en) * | 2006-01-10 | 2007-10-18 | Oto Internat H K Company Ltd | Vibration device for massage device |
CN109974832A (en) * | 2019-04-03 | 2019-07-05 | 浙江华章科技有限公司 | A kind of algorithm of high-speed shaking system amplitude |
CN110948644A (en) * | 2019-12-30 | 2020-04-03 | 淄博松阳锆业科技有限公司 | Ceramic structure shaping vibrating device |
EP4134653A4 (en) * | 2020-04-08 | 2023-09-27 | Fukuoka University | Repeated moment generation device |
Also Published As
Publication number | Publication date |
---|---|
JPH11156296A (en) | 1999-06-15 |
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